Accounting machine



Feb. 16, 1943. p, M|XER 2,311,454

ACCOUNTING MACHINE Original Filed April 25, 1936 4 Sheets-Sheet l FIG.I

INVENI'OR HAROLD I? MIXER BY @eaM ATTORNEY Feb. 16, 1943. H. P. MIXER 2,311,454

ACCOUNTING MACHINE Original Filed April 25,1936 4 Sheets-Sheet 2 FIG.2

mvzuma HAROLD F! MIXER Feb. 16, 1943. H. P. MIXER ACCOUNTING MACHINE Original Filed April 25, 1936 4 Sheets-Sheet I5 FIG.4

INVE "TOR HAROLD P M I XE R A TO RNEY Feb. 16, 1943. I R 2,311,454

ACCOUNTING MACHINE Original Filed April 25, 1936 4 Sheets-Sheet 4 INVENTOR HAROLD P MIXER Patented Feb. 16, 1943 ACCOUNTING MACHINE Harold P. Mixer, Rockville Centre, N. Y., assignor to Remington Band 1110., Bpifalo, N. Y., a corporation of Delaware Original application Apr 76,492, now Patent No. 2

ii 25, 1936, Serial No.

,214,029, dated September 10, 19-40. Divided and this application May 15, 1940, Serial No. 335,214

4 Claims.

The present invention relates to accounting machines and accumulating mechanisms therein of the type which are fully described in my copending application, S. N. 76,492, filed April 25, 1936, now Patent No. 2,214,029, issued September 10, 1940, of which the present application is a division.

The invention more particularly relates to accumulating mechanisms of the creep or crawlcarry type and means for zeroizing the accumulator wheels. These accumulating mechanisms may be used as part of a number of accounting machines used for various purposes. the present use being confined to a multiplying machine fully described in the parent application. This multiplying machine, generally speaking, comprises a sensing mechanism, a multiplication mechanism, a totaling mechanism, punching mechanism and coordinated driving means for the various elements mentioned.

An object of the invention is the provision of a totaling mechanism of the crawl-carry type, which is so constructed that the various wheels associated with the different denominational orders may be substantially simultaneously rotated to their zero positions.

Another object of the invention is the provision of a crawl-carry totaling mechanism which utilizes spur gearing throughout and which, consequently, may drive in either direction.

Another object of the invention is the provision of a totaling mechanism of the crawl-carry type so organized that a very small amount of rotation toward the zero position of a wheel of a lower denominational order may permit the release of the wheel of next higher denominational order for rotation toward its zero stop.

A more clear conception of the further objects, construction, and operation of the invention may be had from the following detailed description when taken in conjunction with the accompanying drawings, in which Fig. 1 is an isometric view of the combined accumulating mechanism and the zeroizing mechanism;

Fig. 2 is an exploded isometric view of the accumulator spur gearing showing the relationship of the accumulator gears and wheels of the planetary transmission for effecting the carry of tens;

Fig. 3 is a plan view of three latch units showing some parts in section;

Fig. 4 is a detail view in elevation showing the mounting of the planetary gearing comprising the carry mechanism on the accumulator gearing;

Fig. 5 is a side view of Fig. 4 disclosing one of the accumulator gears and its associated planetary gears mounted thereon;

Fig. 6 is a front view in elevation of one of the accumulator wheels showing the orbit gear of the planetary train fastened thereto and the sun gear associated with the next higher order likewise fastened to the wheel;

Fig. '7 is a side view of Fig. 6 disclosing the gearing in greater detail;

Fig. 8 is a side detail view with some parts in section showing an assembly of the stop arm, stop bail, release latch, and a pair of contacts cooperating with the stop arm of the highest denominational order accumulator unit;

Fig. 9 is a side detail view showing the stop arm in elevated position together with the accumulator wheel, holding member, and sector locking member;

Fig. 10 is another detail view similar to Fig. 9 except that the parts are shown in another position of operation.

The type of accumulator disclosed in this specification is commonly known as the crawlcarry, as distinguished from the snap-carry type of mechanism in which transfer of tens occurs subsequent to the accumulation operation. In the crawl-carry type, the transfer of tens is continuous and is ordinarily caused by some form of step-down gearing. A common example of the crawl-carry is that shown in the United States patent to Gardner, No. 1,828,180.

In the mechanism of the above patent the transfer is ofiected through the'medium of an eccentrically mounted gear and in taking totals from this mechanism it is necessary that the wheel of the lowest denominational order be positioned against its zero stop before the wheel of the next higher denominational order is released.

In the form of crawl-carry totalizer shown in this application, the carry is through the medium of a train of planetary spur gears and as a consequence the various accumulator wheels may be positioned at the zero stops at substantially the same time.

Moreover, in former crawl-carry mechanism the various wheels were released for return to their zero positions by an independent mechanism, and if a wheel for any reason did not reach its zero position before the next higher order wheel was released, the lower order wheel made practically no further movement after the higher order wheel came against its stop, the result being that one or more of the total positioning members moved less than the correct amount, the total was incorrect and the accumulator was not completely cleared. In the present device various latches cooperate with the accumulator wheels in such manner that normally each wheel is released simultaneously with the release of the latch cooperating with the wheel of next higher order, the wheels thus being released successively and rapidly in fact approaching simultaneous release. The latches then, trip in order and they are delayed only when a nine appears in the accumulator wheel in which case the next higher order wheel is not released until the wheel considered was moved approximately one unit space or to the eight position. This mechanism provides for very nearly simultaneous release of the wheels to zeroize and is a positive means for maintaining the correct relation of the zero stop arm with the stop member on the wheel.

The accumulating mechanism comprises a plurality of accumulator units, together with certain latches for governing their operation. The gears which operate the accumulator units are not indicated in the drawings (except in Fig. 2) since they do not form a part of the present invention. Any gear or sector driven by a calculating mechanism may operate the accumulator units since there is no restriction on timing or phase of operation. In addition to the operating gears which roll numbers into the accumulator units there must be provided a series of sectors (Fig. 1) which, though normally out of mesh, may be brought into mesh with the accumulator gears 2| to operate a rack 22 or other means for recording or printing the total.

The accumulator gears 2| are shown in detail in Figs. 1, 2, 4, and 5 and these wheels together with other accumulator parts are mounted on a common shaft 23 which extends the entire width of the machine and is attached to side frames 29 and 11.

Each accumulator unit (Figs. 1, 2, 4, 5, 6, and '1) comprises the accumulator gear 2|, accumulator wheel 24, together with its integral zero stop and a train of planetary gearing including a sun gear 25, planet gears 21, 28, 30, 3|, and an orbit gear 32.

In an accumulator unit for the lowest denomination order the sun gear 28 is fixed, while in each of the other units the sun gear is fastened to the accumulator wheel 24 and orbit gear 32 of the next lower order.

The accumulator gear 2| (Fig. 2) has thirtysix teeth and is designed to mesh with driving gear 35 which has forty teeth; the exact number of teeth is unimportant, it being necessary only that the ratio of 9 to 10 be maintained.

Fixed to each accumulator gear 2| (Fig. 4) is a stud 33 on which are mounted the gears 21 and 28 which gears are mounted together and rotatably mounted on the stud. Rotatably mounted in and extending through the accumulator gear 2| is a short shaft 34 on one end of which is fixed the planet gear and on the other the planet gear 3| which meshes with the annular orbit gear 32 which is secured to the accumulator wheel 24.

The tooth ratios of the various gears 26 through 32 are such that one turn of gear 26 will produce one-tenth of a turn of gear 32. In the present instance, gears 26 and 21 have thirty teeth each; gear 28 sixteen teeth; gear 30 thirty teeth; gear 3| twelve teeth; and gear 32 sixty-four teeth.

As has been explained above when a digit is to be registered in the accumulator, the drive gear 35 is rotated by external means one tenth of a full revolution for each unit to be accumulated. I

Due to the gear ratio set forth above the rotation of an accumulator drive gear 35 causes its associated accumulator gear to be driven one and one-ninth times as far. Thus, if the digit to be registered is assumed to be 9" the accumulator gear 2| will be driven one and one-ninth times nine-tenths of a complete turn; it 8" then one and one-ninth times eight-tenths, or eight-ninths of a complete turn; and if "1 then one and onenlnth times one-tenth or one-ninth of a complete turn.

The rotation of the accumulator gear 2| rotates the associated accumulator wheel 24 and its integral stop 25 until the stop is properly positioned. The rotation of the accumulator wheel may be considered as the resultant of two separate operations upon it, although actually the two operations occur simultaneously.

One of the component movements of the resultant may be considered as that due to the teeth of planet gear 3| coacting with teeth of orbit gear 32 to pin the two gears together. Due to this component the accumulator wheel 24 will be driven as many ninths of a turn as is the accumulator gear 2|, in an additive direction.

The other component movement of the resultant is that due to the action of the planetary gear train. Thus, if we assume the sun gear 26 of the train to be stationary, which is true of the first, or unit gear, then, as the accumulator gear 2| rotates. the planetary gear 21 will roll on the sun gear 26 and will rotate the orbit gear 32 in the opposite or subtractive direction. Now the gear ratios are such that the orbit gear 32 and, therefore the accumulator wheel 24 tend to rotate one-tenth as much as the accumulator gear 2| in the opposite direction.

The resultant and actual motion of the accumulator wheel 24 for any digit is, then, the motion of the accumulator gear 2| minus one-tenth of that amount. Thus, for a digit 9 the accumulator wheel rotates one turn minus one-tenth of a turn or nine-tenths of a turn; for the digit 8", the wheel rotates eight-ninths of a. turn minus eight-ninetieths of a turn, or eight-tenths of a turn and for the digit 1 the accumulator wheel rotates one-ninth of a turn, minus oneninetieth of a turn, or one-tenth of a turn.

From the above, it will be seen that an accu mulator wheel during accumulating operations rotates as many tenths of a turn in an additive direction as the digit registered represents.

In addition to movement imparted to it from the associated accumulator gear 2|, each accumulator wheel 24 (except that of the lowest denominational order) has imparted to it movement due to the rotation of the sun gear 26 attached to the accumulator wheel of the next lower denominational order. In this action, the

- gears 26, 21, 28, 3|], 3|, and 32 act as ordinary step-down gearing, and serve to rotate each accumulator wheel one-tenth as far in the same direction as the wheel of the next lower order. For example, if the wheel of the lowest or units order were rotated nine-tenths of a turn to register a nine" and no digits were inserted in the higher order wheels, then the wheel of the tens order would rotate nine one-hundredths of a turn, that of the thousands order nine onethousandths, that of the ten-thousands order nine ten-thousandths, etc. The movement of any wheel is, then, the sum of the movements imparted to it from its associated accumulator gear and the correct decimals of the movements imparted to all lower order wheels. these decimals being in each case the movement of any wheel divided by ten to that power which represents the degree of removal of the lower order wheel from the higher order. the movement of which is sought.

To explain the above statement more fully, let us assume that the units, tens. and hundreds orders of accumulator gears are rotated ninetenths, seven-tenths, and five-tenths of a turn, respectively. Then the hundreds wheel will be rotated fivetenths of a turn plus seven-tenths divided by (10) turns plus nine-tenths divided by (10) or .579 turns.

It will thus be obvious that the total rotation of any accumulator wheel 24 is the sum of the rotative movement transmitted to it. due to movement of the next lower order accumulator wheel and the movement transmitted to it due to movement of its own accumulator gear.

The stops 25, being integral with the accumulator wheels, move therewith; these stops occupy approximately one-tenth of the periphery of the wheels and, as will be shown later, cooperate with stop arms to govern the positioning of recording members and to release total latches.

Accumulator zeroizing mechanism The present calculating machines which employ the herein described accumulator operate in two phases. The first phase stores or accumulates numbers in the accumulator due to the operations of the driving gears 35. These driving gears may be a part of an adding machine, multiplying machine or any other calculating mechanism and said wheels may operate in an additive or subtractive direction, During the first or accumulating phase the sector gears 20 (Fig. 1) are pulled out of mesh with the accumulator gears 2| by any convenient means. Fig. 1 shows a slot cam 36 cut in an arm 31 which positions a shaft 38 on which the sectors 20 are rotatably mounted. Movement of arm 31 causes the sectors to be moved in or out of mesh in accordance with a predetermined schedule of operations which have been fully described and disclosed in the parent application of which this is a division. It should be understood, however, that any mechanism which will shift from the driving gear to the zeroizing or totaling gear may be used with this accumulator.

The present accumulator contemplates a second or total taking phase which comprises the rotation of the accumulator wheels in a reverse direction until the stops 25 (Figs. 1, 2, 6, I7, 9 and 10) thereon strike stop arms 40 located at definite points or until they reach the zero position. This rotation is effected after the accumulator wheels have been meshed with a series of sectors 20 and the action is caused by a series of springs which urge the ratchet bars 61 toward the front of the machine.

In prior crawl type accumulators. it was customary to mesh all the accumulator gears with the associated toothed elements while those elements were prevented from moving, and to then release the toothed elements one by one progressively from the lowest to the highest order, the mechanism, governing the timing of the progression being independent of the stop arms, the interval between successive releases being suflicient for a wheel to travel the maximum amount, namely, from 9 to The instant mechanism is so constructed that a total arm governs the release of the toothed element associated with the next higher order wheel and release of the total arm associated with that wheel, thus eliminating the independently operated timing mechanism, and speeding up the return of the accumulator wheels to their zero position. Since, in the present device, the creep or crawl is effected through the medium of planetary spur gearing, the position of an accumulator gear is adjusted in accordance with the position of the wheels of lower order after those wheels have reached their true zero position and thus it is not necessary to provide time for each wheel to reach its zero position before releasing the wheel of next higher order. In most instances, the wheels will be released in immediate progression. delay being involved only when a wheel is in the 9 position. It will 'be obvious that, if all wheels had nines registered thereon, the higher order wheels would, due to the creep or crawl, stand very near the zero point, and that, when the stop arm was lowered into the path of the stop, it might, and probably would, stop it at its zero point, rather than at its nine point.

In order to eliminate this possibility of error. each zero stop occupies a peripheral space substantially equal to a unit, so that the stop arm 40 cannot drop and release the toothed element associated with the order until the wheel has rotated one-tenth of a turn.

The mechanism for releasing the accumulator Wheels in order and for delaying such release will now be described.

Pivoted on a rod 4| (Figs. 1, 2, 8, 9, and 10) extending between the carriage side plates (not shown) are a number of stop arms 40, one for each accumulator unit. These stop arms are formed as bell-cranks and each one is provided with a bent-over lug 42 on its substantially horizontal arm and a stud 43 on its vertical arm. Each bent-over lug 42 lies in the same vertical plane as the zero stop 25 on the accumulator wheel of corresponding denominational order so that, when the stop arm 40 is rotated clockwise (Fig. 9). the lug 42 lies in the path of the stop 25 on wheel 24 and causes the wheel to stop at its zero position.

Pivoted on the rod 4| (see Fig. 1) adjacent to each stop arm 40 is a holding member 44 which serves to hold the sector, or other toothed element against movement and also serves to hold the stop arm 40 of the associated accumulator unit against clockwise rotation.

Each holding member 44 is formed as shown in Figs. 1, 2, 8, 9, and 10, it being substantially L-shaped, having a horizontal arm 45 and a vertical leg which has a lug 4'6 bent to the left from the side thereof, and a lug 41 bent to the right from the opposite side. The horizontal arm 45 cooperates with a restoring bail 43. The bottom of holding member 44 is formed with an extending foot and is adapted to cooperate with a lug 51 formed on a sector locking member 53. The locking member is pivotally mounted on shaft 52 and cooperates with a pin 54 on the sector 20 to hold it from rotation when held down by the foot 50 (see Fig. 9).

Lug 46 lies in front of the vertical leg of stop arm 40 so that, when the holding member 44 is in its normal position (as shown in Figs. 2 and 9) the stop arm 40 is held against clockwise rotation or out of the path of the associated zero stop 25.

The lug 41 (Fig. 9) is positioned in front of the end of the right-hand arm 51 of latch 56. The foot 50, when in normal position lies directly above lug 5| on sector locking member 53, thereby preventing the release and subsequent operation of the sector2li by the spring tension applied thereto.

Release latch 58, as shown in Fig. l, is a ushaped piece having arms 55 and 51 integral with each side of the U, and having a lug on one side to which a spring may be attached. The latches 56 are pivoted on a rod 58 extending between the side frames, the rod being so located that, when the release latches are in normal position (Fig. 9), the rearward end of the left-hand arm 55 abuts the right-hand lug 41 on holding member 44 of an accumulator unit, while the horizontal portion of the cam surface on the right-hand arm lies above the stud 43 on the stop arm 40 associated with the accumulator unit of lower order.

When a total is to be taken the toothed ele ments, in the present instance the toothed sectors 20, are caused to be meshed with the accumulator gears 2|, while being held against rotation (as they go into mesh) by studs 54 thereon positioned in notches in locking members 53.

At this time the bar or bail 48 is raised by a link Bil (Fig. l) which is operated by a cam (not shown) in the base of the machine and all the holding members 44 are released for clockwise rotation in so far as control by the bail is concerned. The members 40 and 44 are now under control of the U-shaped release latches 55. However, only the lowest order holding member is free to move at this time for it is the only one not blocked by a release latch 55.

When released, the holding member 44 is rotated in a clockwise direction by a spring 6| (Figs. 2 and 8) stretched between a stud and an anchor bar (not shown).

Thus, when upon taking a total the ball 48 is raised, holding member 44 rotates, and the foot 50 thereon moves off the lug on looking member 53. Although member 53 is still urged downwardly (due to a spring 62 stretched between a forward extension thereof and an anchor bar) a strong spring (not shown) tends to rotate the sector clockwise and consequently the stud 54 cams the locking member 53 upwardly and the sector is free to rotate. If the associated accumulator wheel 24 at this time lies in any position other than that representative of "9, the stop arm 40 (which is urged clockwise by a spring 63 stretched between stud 43 and an anchor bar) immediately moves clockwise until the lug 42 thereon rests on the periphery of the accumulator wheel 24. If, however, the wheel should be in the 9 position, the lug strikes the top portion of stop thereby preventing the complete oscillation of stop arm 40 until the stop 25 has been rotated so that the Wheel 24 reaches the "8 position.

When the stop arm 40 rotates (see Figs. 9 and 10) the stud 43 thereon strikes the camming surface on right-hand arm 51 of release latch 56, causing it to rise and the rearward end of its left-hand arm 55 is removed from the path of the lug 41 on the holding member 44 of the next higher denominational order. This second holding member rotates clockwise and releases the associated stop arm 4|) and sector locking member 53 of the adjacent higher order. Again the stop arm 40 moves, immediately if the wheel stands at a position other than nine, (and after a slight delay if at nine position) and, when it moves, sets up a similar train of operations to release the next adjacent higher order wheel and stop arm. This action continues from one accumulator unit to another until all wheels are released.

It will be seen from the above that, if the accumulator wheels of lower denominational orders have therein digits greater than those in the wheels of higher denominational orders, then the wheels of higher orders may reach their zero positions first.

In the older type of crawl and carry mechanism, embodying the eccentric transmission, such operation would be fatal because the higher denominational order wheels once positioned could not be corrected, and, since they would be positioned before the creep from the lower denominational order wheels was taken out, their final reading or positioning would be incorrect.

Due to the planetary spur gear arrangement the present device is operative under conditions such as set forth. If a wheel of higher denominational order reaches its zero position before those of lower denominational orders, then, as the lower order wheels come to their zero positions, they cause readjustment of the accumulator gear and sector of the higher order unit.

If, for example, the units order wheel has in it a digit of greater value than that in the tens order Wheel, then, after both have been released, the tens order Wheel will reach its zero position first. In moving to its zero position the tens order wheel will permit the sector (or other toothed element) associated therewith to move too far and the sector will be incorrectly positioned.

As the units order wheel continues to move towards its zero position, the sun gear 26 of the tens order unit is carried therewith. As the sun gear rotates it also rotates the step-down gearing, comprising planetary gears 21, 28, 30, and iii with it, the gears 26 and 3| both rotating counterclockwise. Since the orbit gear 32 is prevented from rotating, due to the fact that stop 25 is against the stop arm 40, the accumulator gear 2| is forced to move clockwise and in so moving forces the sector 20 of the tens order to be readjusted to the proper position.

Le it be assumed, now, that the numbers and 189 are inserted in the accumulator wheels in two successive accumulating operations, giving a total of 269.

After the first accumulating cycle the units order wheel stands at zero, the tens order wheel at 8 (0.8 of a turn), etc.

After the second accumulating cycle the units order wheel stands at "9 (0.9 of a turn), the tens order wheel at 6.9 (0.69 of a turn, since it stood at 0.8 and had added to it 0.8 and 0.09), and the hundreds order wheel at "2.69 (0.269 of a turnit stood at 0.08 of a turn and had added to it 0.1 turn carry from the tens order plus 0.08 or a turn also carry from the tens order and 0.009 of a turn carry from the units order).

The units, tens, and hundreds order wheels thus stand at 9", 6.9, and 2.69, respectively.

If a total is now initiated, or, more exactly, if the ball 48 is raised, the stop arm 40 of the units order will be released for clockwise rotation, (see Figs. 9 and 10), but, since the stop 25 is in the 9 position, the lug 42 will strike the periphery of the stop and the arm will be prevented from moving. However, bail 48 also released holding member 44 and thus caused the release of the sector 20 of the units order.

When the sector has moved through one unit space, the wheel of the units order will also have moved through one unit space and will lie at 8, the tens wheel at 6.8, and the hundreds wheel at 2.68.

Although the wheels 24 of the tens and hundreds order are free to move, the corresponding sectors are held by their locking members 53. All the movements of these wheels are caused by the planetary gearing of the units carry mechanism.

When the units wheel reaches 8, the stop arm 40 associated therewith drops, since the stop has passed by. This movement of the units stop arm permits holding member 44 to move, camming arm 57 upward and raising arm 55 out of the path of lug 41 of the tens holding member 44, permitting it to rotate clockwise and release the tens order sector 20. The stop arm of the tens order immediately moves and releases the hundreds order sector. At this time the units order sector will have moved one unit space while other sectors will not have moved.

Assuming, for convenience, that the sectors of the tens and hundreds order are released simultaneously and that this release is at the moment when the units order wheel reaches its 8 position, then it is obvious that the hundreds order wheel will reach its zero position before either the tens or units order wheels.

The movement of the hundreds order wheel toward its zero stop is comprised of movement transmitted from its own sector and gear and movement transmitted from the gears and sectors of lower orders. These movements may be computed since the gear ratios are known, the

movement, of course, is in a subtractive direction bringing the stops 25 towards the stop arms rather than away from them as in accumulating cycles.

If, now, we assume that all sectors move at the same speed and, consequently, the same amount in a given time (this is a probable condition for the springs, the friction, etc., of the various units are substantially equal) then the movement of the sectors 20, or equivalent toothed elements, may be taken as the same for all and equal to X. Now X units of movement of a sector cause X units of movement of the corresponding accumulator wheel,

units of movement of the next higher order wheel and units of movement of the second higher order wheel. Then, the units of movement of the wheel of the hundreds order, to bring it to 0, namely, 2.68 equals the movement of its own sector, or X plus of the movement of the tens order sector, or

wheel truly stands at "0, we find that the wheel has moved 2.414 plus .2414 plus .02414 or 2.680 which, subtracted from 2.68, =0.

Now, the tens order wheel at this time will have moved 2.414 plus .2414, or 2.655. Since it stood at 6.8 it now stands at 6.800 minus 2.655 or 4.145.

At the same time the units order wheel will have moved 2.414 and since it stood at 8.000, will now stand at 8.000 minus 2.414 or 5.586.

Also, at this time the hundreds, tens, and units sectors will have moved from their zero positions, respectively, 2.414, 2.414, and 3.414 units. It will be remembered that the units wheel moved one unit to clear the stop arm and start the totaling operation.

Now the tens and units order wheels will continue to rotate and after the tens order wheel has rotated through 4.145 unit spaces it will come to rest with its stop against the stop am. In order that the wheel rotate through 4.145 units the tens and units sectors must move X unit spaces. Now,

and, therefore, X:3.768.

Again checking, we find that the tens order wheel rotates 3.768 plus 0.3768 or 4.145 units bringing it to zero. The units order wheel will have rotated 3.768 units and will now stand at 5.586 minus 3.768 or 1.818 units from zero.

As the tens order wheel rotated to zero it rotated the hundreds order sun gear 26 with it (counter-clockwise as seen in Fig. 2), and this tended to rotate the hundreds order orbit gear 32 counter-clockwise. But the stop 25 being already against the stop arm, the orbit gear could not move counter-clockwise and consequently the accumulator gear 2| was caused to move in the opposite direction (clockwise) one-ninth as many times as the sun gear or .0460 turn. Now, each one-ninth of a turn of the gear 21 represents a unit and consequently the gear 2| and its associated sector 20 will have moved nine times 0.0460 unit or 0.414 unit.

In order to show clearly that, when an accumulator wheel 24 has reached its zero stop arm, the correction of the associated accumulator gear 2| by the accumulator wheel 24 of the next lower order is one-ninth of the movement of the latter wheel, the following explanation is given:

The sun gear 26 will move as many fractions of a turn as does the wheel of the next lower order since the sun gear is fastened to that wheel. Then the pinion 30 of the higher order tends to rotate the orbit gear 32 of that order one-tenth the number of turns of the sun gear. But the orbit gear 32 of the higher order cannot rotate counter-clockwise since the stop 25 thereon is against the stop arm and consequently the accumulator gear 21 of the higher order rotates clockwise one-tenth the number of turns of the wheel of lower order. In so doing the accumulator gear carries the planet gear 21 with it, causing the-gear to roll on the adjacent sun gear, and thus tending to move the orbit gear again, this time one one-hundredth the number of turns of the lower order accumulator wheel. Again this results in rotating the higher order accumulator gear clockwise and in rolling the planet gear 21 on the sun gear 25. Now the planet gears 30 and 3| again tend to rotate the orbit gear and to again rotate the accumulator gear, this time, of course, one one-thousandths the number of turns of the sun gear; and this action continues until all have reached normal.

Now the accumulator gear will have moved one-tenth, plus one-hundredth, plus one-thousandths, plus, etc., or will have moved a number of turns represented by the repeating decimal .l11l--- this repeating decimal equals one-ninth and thus it is seen that the movement of the higher order accumulator gear is one-ninth that of the lower order accumulator wheel.

Now the sector moves with the accumulator gear and, since it stood at 2.414 and has just moved 0.414 toward 0, it now stands at 2.000 which is correct.

At this time, the hundreds and tens wheels are at and the units wheel 1.818 units from 0, also at this time the sectors stand 2, 6.182 (2.414 plus 3.768), and 7.182 (3.414 plus 3.768) units from zero.

The units accumulator wheel is now 9 minus 7.182 or 1.818 units from 0.

To rotate it this amount, its sector must move this amount. In moving 1.818 units the unit wheel is brought against the zero stop. Also the sun gear of the tens order rotates 1.818 units counter-clockwise and tends to rotate the orbit gear of that order counter-clockwise 0.1818 units. Since this is prevented, due to the stop lying against the stop arm, the gear 2| rotates 0.1818 (.00202 turn) clockwise and thus the tens sector is moved .1813 unit toward 0. Now, the tens sector stood at 6.182 and this minus .1818 equals 6.00 which correctly positions the sector.

The units order sector has moved one unit plus 2.414 units plus 3.768 units plus 1.818 units and is, therefore, positioned at 9, which is correct.

As has been stated above, the recording means which punches or prints the total derived from the accumulator wheels 2| may be of any convenient construction and is not a part of this invention. Fig. 1 indicates one way in which such a means may be constructed. The sectors 20 which are meshed with the accumulator gears 2| just prior to total taking, position a rack 22, said rack cooperating with a smaller gear 64 attached to the sector 20. A disc 65 and a shroud plate 66 hold the gear and rack in proper spaced relation. At one end of the rack 22 a ratchet bar 61 is attached for positioning a plurality of recording devices not shown in the drawings.

It is quite necessary that the total taking or zeroizing mechanism be shifted in and out of mesh with the accumulator gears when the operating phases are changed from accumulating to total taking and back again. It is also necessary to disengage the driving mechanism at some point so that a total may be rolled out of the accumulator easily and quickly. Since the driving means comprises a series of mechanical clutches which are normally disengaged, further disengaging means is not necessary.

Fig. 2 shows a driving gear permanently meshed with the accumulator gear 2 I. A detent wheel 68 is secured to said driving gear in order to register the digit more accurately. A detent roller 10 is mounted on a lever H, which, in turn, is rockably mounted on a shaft 12 and urged counter-clockwise by a spring 13. When a total is to be rolled out of the accumulator unit, all the detent levers (there is one for each drive gear) are pulled away from the detent wheels 68 by mechanism not shown in the drawings, but fully disclosed and described in the parent application. Such an action is not necessary to the successful operation of the device but the speed of total taking is increased and the operation is more quiet.

Fig. 8 shows the stop arm 40 of the highest order accumulator together with its associated mechanisms. This stop arm is the last one to be operated and within a very short time after the arm 40 has descended the total taking operation is at an end and the machine is ready to change its phase of operation to either another accumulating cycle or else a printing or punching phase.

To initiate the new phase of operations a pair of contacts 74 is positioned to the left of the highest order stop arm attached to spring arms 15 and 15 and secured by the usual insulating means to the left side frame 11. A lug I8 is attached to the upper spring arm 15 in such mannet that it projects under the stop arm 40 and is engaged by it when the stop arm is lowered.

The contacts 14 may initiate a new phase of operations in a number of ways such as by relays, magnetic clutches or solenoid operated gear change devices. These are not shown and do not form a part of the present invention.

While I have described what I consider to be a highly desirable embodiment of my invention, it is obvious that many changes in form could be made without departing from the spirit of my invention, and I, therefore, do not limit myself to the exact form herein shown and described, nor to anything less than the whole of my invention as hereinbefore set forth, and as hereinafter claimed.

What I claim as new, and desire to secure by Letters Patent, is:

In a computing machine of the class described, having an accumulator with a tens carry mechanism of the crawl type, an accumulator ear and an accumulator wheel for each de nominational order, a zero stop lug on each accumulator wheel, a stop arm operable to engage said zero stop lug when the accumulator is being set to zero, means for retaining the stop arm in non-engaging position only when the accumulator wheel stands between the nine and zero position, means tending to restore the accumulator gears to zero, a tripping lever in each order adapted to be tripped when the stop arm in that order is moved to engaging position, a release latch in each order controlled by the tripping lever for releasing the stop arm in the next higher order, and a locking mechanism controlled by the stop arm for holding the restoring means until the stop arm is moved to the engaging position.

2. In a computing machine of the class described, having an accumulator with a tens carry mechanism of the crawl type, an accumulator gear and an accumulator wheel for each denominational order, a zero stop lug on each accumulator wheel, a stop arm operable to engage said zero stop lug when the accumulator is being set to zero, means for holding said stop arm in non-engaging position only when the accumulator wheel stands at a position between nine and zero, restoring means tending to reset the accumulator wheels to zero, a tripping lever in each order operable by the stop arm in that order, a release latch in each order controlled by the tripping lever for releasing the stop arm in the next higher order, a locking mechanism controlled by the stop arm for releasing the restoring means when the accumulator wheels are to be zeroized, a bail for holding all of said stop arms in non-engaging position while amounts are being entered into the accumulator, and means for removing said ball when the accumulator wheels are to be zeroized.

3. In a computing machine of the class described, having an accumulator with a tens carry mechanism of the crawl type, an accumulator gear and an accumulator wheel for each denominational order, a zero stop lug on each accumulator wheel, a stop arm operable to engage said zero stop lug when the accumulator is being set to zero, said stop lug adapted to hold the stop arm in non-engaging position for only one-tenth of a revolution of the accumulator wheel, restoring means tending to reset the accumulator wheels to zero, a tripping lever in each order controlled by the stop arm in that order, a release latch in each order controlled by the tripping lever for releasing the stop arm in the next higher order, a locking mechanism controlled by the stop arm for holding the restoring means until the accumulator wheels are to be zeroized, a bail for holding all of said stop arms in nonengaging position while amounts are being en tered into the accumulator, and means for removing said bail when the accumulator wheels are to be zeroized.

4. In a computing machine of the class described, having an accumulator with a tens carry mechanism of the crawl type with spur gearing, an accumulator gear and an accumulator wheel for each denominational order, a zero stop lug on each accumulator wheel, said stop lug extending for not more than one-tenth of the periphery of said accumulator wheel, a stop arm operable to engage said zero stop lug when the accumu lator is being set to zero, a rack in each order which is coupled to the accumulator gear when the accumulator wheel is being set to zero, a tripping lever in each order controlled by the stop arm in that order, a release latch in each order controlled by the tripping lever for releasing the stop arm in the next higher order, said tripping lever and release latch comprising means for holding the higher order stop arms in unengageable position until after the lower order stop arm is in engageable position.

AROLD P. MIXER. 

